EP0771614B1

EP0771614B1 - Powered clamp apparatus

Info

Publication number: EP0771614B1
Application number: EP96307709A
Authority: EP
Inventors: Edwin George Sawdon
Original assignee: BTM Corp
Current assignee: BTM Corp
Priority date: 1995-10-30
Filing date: 1996-10-24
Publication date: 2003-08-13
Anticipated expiration: 2016-10-24
Also published as: EP0771614A3; EP0771614A2; DE69629437T2; DE69629437D1; CA2188517A1; US5884903A; MX9605197A

Description

This invention relates generally to an apparatus for positioning or clamping a workpiece according to the preamble of claim 1 and to a method of operating a workpiece engaging device according to the preamble of claim A (see, for example, US-A-5 171 001).
Powered clamps are commonly used in industrial applications for holding work pieces of many sizes and shapes during forming and machining operations. Such devices typically include a pneumatically or hydraulically actuated cylinder which causes one or more arms to move through a desired range of rotational motion to push against a work piece. Depending on the specific application, the user may wish to actuate one or two arms which may be vertically or horizontally aligned in an environment contaminated with weld splatter, saw chips, coolants, dust and dirt. One such conventional powered clamp is disclosed in U.S. Patent No. 5,171,001 entitled "Sealed Power Clamp" which issued to the present inventor on December 15, 1992.
Other traditional powered clamps are disclosed in the following U.S. Patents: 4,905,973 entitled "Power Operated Clamp With Externally Mounted Adjustable Clamp Arm" which issued to Blatt on March 6, 1990; 4,637,597 entitled "Locking Power Clamp" which issued to McPherson, et al, on January 20, 1987; 4,496,138 entitled "Power Operated Clamp" which issued to Blatt on January 29, 1985; 4,494,739 entitled "Power Operated Rotatable Clamping Assembly" which issued to Valentine on January 22, 1985; 4,458,889 entitled "Locking Power Clamp" which issued to McPherson, et al, on July 10, 1984; 4,021,027 entitled "Power Wedge Clamp with Guided Arm" which issued to Blatt on May 3, 1977; 3,702,185 entitled "Cylinder Operated Power Clamp" which issued to Blatt on November 7, 1972; and 3,570,835 entitled "Power Operated Clamping Device" which issued to McPherson on March 16, 1971. A limitation of these traditional clamps is that the arms will typically move or release pressure upon the work piece when fluid actuating pressure is reduced or lost. Furthermore, the machining tolerances must be accurately controlled among the majority of internal clamp component parts in order to achieve the desired component part motions and to achieve satisfactory clamping forces.
GB-A-2 082 945 discloses a clamp comprising: a body; a generally linearly movable powered actuator disposed in said body; a movable slider block coupled to said actuator for movement in advancing and retracting directions, a first stop surface located on said slider block; a link pivotally coupled to said slider block; a crank pivotally coupled to said link; and a work-engaging arm coupled to said crank and extending exteriorly from said body, said crank having a second stop surface engagable with said first stop surface on said slider block.
According to a first aspect of the present invention there is provided an apparatus for positioning or clamping a workpiece according to claim 1.
According to a second aspect of the present invention there is provided a method of operating a workpiece engaging device, the method comprising the steps of:
(a) moving a first member in a first direction in response to an actuator applying an actuating force;
(b) moving a second member in a second and rotational direction about a fixed axis in direct response to movement of said first member; and
(c) stopping the rotation of said second member by rotating the second member until said second member abuts against said first member to at least temporarily lock said second member against rotation in both the advancing and retracting directions regardless of the presence of an actuation force.
The hereinafter described and illustrated preferred embodiments of powered clamp and gauging apparatus include a tapered self-locking feature for holding a rotated arm even after loss of piston actuating pressures. Thus, workpieces will not fall from their locked and/or gauged positions, preventing workpiece and equipment damage. A further feature of the preferred embodiments is that slotted coupling between moving members allows for a toggle action which magnifies clamping forces without adversely affecting apparatus accuracy for gauging. A yet further feature of the preferred embodiments is the employment of a specifically configured slide and crank in combination with a lost motion device in order to maximise unlocking forces while reducing the need for accurate component parts of machining tolerances. These more relaxed tolerances provide for lower cost manufacturing and reduced part scrappage while improving clamping and gauging force efficiencies and performance.
The illustrated preferred embodiments of apparatus are fully sealed and permanently lubricated and are therefore suitable for use in even the most contaminated environments. The embodiments of apparatus are also very compact and lightweight and can have their clamping or gauging arm easily preset to any one of a number of positions.
Embodiments of apparatus in accordance with the present invention will now be described, by way of example only, with reference to the accompanying drawings, in which:
Figure 1 is a perspective view showing the preferred embodiment of a powered damp and gauging apparatus of the present invention;
Figure 2 is a side elevational view, taken partially in section, showing the preferred embodiment of the present invention;
Figure 3 is an exploded perspective view showing the preferred embodiment of the present invention;
Figure 4 is a fragmentary side elevational view showing the preferred embodiment of the present invention;
Figure 5 is an end elevational view showing the preferred embodiment of the present invention with a cover plate removed;
Figure 6 is a side elevational view showing a piston rod employed in the preferred embodiment of the present invention;
Figure 7 is a side elevational view showing a crank employed in the preferred embodiment of the present invention;
Figure 8 is an end elevational view showing the crank employed in the preferred embodiment of the present invention;
Figure 9 is a fragmentary true elevational view, taken in the direction of arrow 9-9 in Figure 7, showing the crank employed in the preferred embodiment of the present invention;
Figure 10 is a side elevational view showing a slide employed in the preferred embodiment of the present invention;
Figure 11 is a bottom elevational view showing the slide employed in the preferred embodiment of the present invention;
Figure 12 is an end elevational view showing the slide employed in the preferred embodiment of the present invention;
Figures 13A is a diagrammatic side view showing an arm employed in the preferred embodiment of the present invention disposed in a toggled clamping position;
Figures 13B - 16 are a series of diagrammatic side views showing various operating positions of the preferred embodiment of the present invention;
Figure 17 is a diagrammatic side view showing a first alternate embodiment of the present invention;
Figure 18 is a diagrammatic side view showing a second alternate embodiment of the present invention; and
Figure 19 is a diagrammatic side view showing a third alternate embodiment of the present invention.
Referring to Figures 1 - 5, the preferred embodiment of a powered clamp and gauging apparatus 31 of the present invention includes a body 33, an actuator 35, a slide 37, a link 39, a crank 41, a hub 43 and an arm 45. Arm 45 is located external to body 33 while the other afore-referenced components are internally disposed within body 33. Arm 45 can be reversed to attach to a face of hub 43 on either side of body 33. Alternately, a pair of arms can be coupled to both faces of hub 43.
Body 33 is forged or extruded and then machined from 6061-T6 aluminum as a unitary hollow part. An end cap 51 is fastened upon a proximal end of body 33 while a 1008/1010 steel front cover 53 is screwed upon an open proximal end of body 33. Silicon seals and elastomeric o-rings, or the like, are disposed between end cap 51, front cover 53 and body 33. After the machining and internal component assembly, a cavity 55 within the distal end of body 33 is then packed with grease and sealed by front cover 53. Thus, the one piece nature of body 33 aids in achievement of a fully sealed and permanently lubricated powered clamp.
Actuator 35 includes a piston 61 and an elongated, cylindrical piston rod 63. Piston 61 is linearly moveable within a longitudinally oriented cylindrical bore 65 machined in body 33. Piston linearly strokes in response to pneumatic or hydraulic fluid pressures forcing piston 61 in either longitudinal direction. Various annular and elastomeric seals 67 are provided between portions of actuator 35 and the coincidental bores within body 33.
As can best be observed in Figures 3, 6 and 10-12, slide 37 has a generally cylindrical peripheral surface 71 interrupted by a bifurcated abutting surface 73 and a longitudinally extending internal chamber 75. Abutting surface 73 is preferably machined with a 3° self-locking Morse taper or inclined angle. Other locking taper angles may be used depending upon the specific material coefficients of friction. A transversely oriented and longitudinally elongated slot 77 is cut within a trailing end of slide 37. A distal end of piston rod 53 internally projects within a cylindrical and longitudinally oriented passageway 79 in the trailing end of slide 37. The distal end of piston rod further has a transversely oriented cylindrical hole 81. A roll pin 83 movably extends through transverse slot 77 in slide 37 and firmly engages with hole 81 in piston rod 63. Hence, lost linear motion or travel, of approximately 6.35 mm (0.250 inches), is accomplished between actuator 35 and slide 37. In other words, piston 61 can begin return stroke movement prior to coincidental following rearward movement of slide 37.
A leading end of slide 37 additionally has transversely oriented cylindrical openings 91 intersecting with internal chamber 75. Slide is made from 41L40 CF material which is hardened and ground to RcC 38-42. Piston rod 63 is made from 1045 chrome plated material with a threaded proximal end for engagement with the piston. Locktite adhesive is applied to the threads. Although not preferred, transverse slot 77 and transverse cylindrical openings 91 can be reversed between the piston rod and slide.
Referring now to Figures 3 arid 7-9, an aperture 101 within a first end of elongated link 39 is aligned between openings 91 of slide 37 for engagement by a 12L14 CDS material link pin 103 for pivotable movement thereabout. A pressfit pin 105, set screw or the like engages a circumferential groove 107 to affix link 39 to link pin 103. An aperture 109 in the opposite end of link 39 is aligned between a pair of driven journalling openings 111 within parallel walls 113 of crank 41. Openings 91 within slide 37 are transversely elongated opposite from transverse slot 77. Furthermore, openings 91 have a vertically elongated dimension greater than the diameter of link pin 103; this allows for a toggle action as will be discussed in greater detail hereinafter. Alternately, openings 91 may have a circular configuration while aperture 101 of link 39 is given an elongated slot-like shape. Another link pin 115 and fastening pin 117 pivotally affix link 39 to a driven journalling segment of crank 41. Link 39 is preferably made from 4140 HRS material.
Crank 41 further has a seat 121 from which said walls 113 extend in a bifurcated manner. A 3° self-locking Morse tapered contact surface 123 upwardly projects from seat 121 while second and third 3° self-locking Morse tapered contact surfaces 125 upwardly extend near the driven journalling segment of crank 39. A partially circular trough 127 spans between contact surfaces 123 and 125. A semi-circular recess 129 is disposed in an opposite edge of crank 41 from contact surfaces 123 and 125. Moreover, four orifices 131 transversely extend through seat 121 and are arranged in a generally semi-circular pattern in relation to each other and border about recess 129. Crank 41 is preferably machined from 6150 HRS material which is hardened and ground to Rc 50-54.
As is shown in Figures 3-5, hub 43 has a cylindrically shaped peripheral surface 131 partially split by a laterally extending channel 133. Hub 43 further has an annular flange 135 outwardly projecting from an outboard face. Peripheral surface 131 of hub 43 is rotatably received within a matching cross bore 137 through side walls of body 33. Eight circularly oriented holes 139 are drilled through both faces of hub 43 and the portion of hub 43 adjacent to channel 133. A central hole 151 is also drilled through the entire hub 43. Hub 43 is preferably machined from 41 L40 CF material.
Arm 45 is affixed to a face of hub 43 through four dowel pins 171 and a screw or stud 173. Screw is received within central hole 151 of hub 43. Screw 173 engages with a locking nut and sandwiches a washer on its opposite end. Nut is torqued to approximately 45 pounds-foot. Recess 129 of crank 41 is designed to provide clearance around the shaft of screw 173. Arm 45 has a set of apertures 175, arranged in a generally circular pattern with respect to each other, for receiving ends of dowel pins 171 when arm 45 is placed in its preselected orientation in relation to hub 43 and body 33. Four roll pins 172 also retain hub 43 to crank 41. Arm 45 is preferably machined from 6150 HRS RcC 50-54 material. A 4150 HT material hub cap is placed over the opposite side of cross bore 137, the washer and flange 135 of hub 43 if a second arm is not attached.
A first alternate embodiment lost linear motion device 201 employed within the present invention powered clamp 31 is illustrated in Figure 17. In this embodiment, a piston rod 203 has a distal end with a constricted shaft 205 depending therefrom upon which is mounted a transversely expanded, cylindrical head 207. The mating slide 209 has a partially cylindrical receptacle 211 in its trailing end from which longitudinally extends a shaft passageway 213. Head 207 is placed within receptacle 211 and shaft 205 is placed within passageway 213. Furthermore, head 207 has a transversely larger dimension than passageway 213. The lost linear motion function is accomplished by receptacle 211 having a larger longitudinal dimension than that of head 207.
The sequence of operational steps can be observed with reference to Figures 13B-16. Specifically, Figure 13B shows arm 45 disposed in a locking position wherein a work piece would be firmly held for a highly repeatable and accurate gauging function. In this locking position, piston 61 is near but does not bottom out or contact against a forward face 251 of bore 65. There is a longitudinal gap between piston 61 and face 251. In this forward piston position, slide 37 is linearly stopped prior to stoppage of piston 61 due to abutting against crank 41, such that piston rod 63 and pin 83 are moved toward a leading end of transverse slot 77 of slide 37. In other words, piston 61 advances until crank 41 engages in a frictionally self-locking manner against slide 37. Therefore, slide 37 becomes wedged between crank 41 and upper wall of body 33 as a result of the inclined tapers.
Concurrently, link 39 is oriented in a generally vertical direction (as illustrated) while crank 41 is disposed in a locked position. In this locked position, contact surfaces 123 and 125 press against tapered abutting surface 73 of slide 37 in a self-locking manner. Therefore, crank 41 maintains the locked position of hub 43 and arm 45 thereby preventing them from moving even if piston actuating pressures are reduced or lost. This is much more accurate and repeatable than having a rotating member simply abut against the body or some other fixed element.
Figure 13A shows a full clamping position similar to that of Figure 13B except that the clamping action of arm 45 retains a workpiece 231 against a work surface 233 and self-locking of crank 41 against slide 37 is prevented. However, a force multiplying toggle motion is achieved by link 39 and link pin 103 rising to the top of elongated openings 91 of slide 37. Hence, the present invention provides for both accurate gauging and strong clamping functions within a single apparatus.
By comparing the component positions of Figure 14 to those of Figure 13B, it can be observed that piston 61 and piston rod 63 are linearly pulled rearward without a coincidental movement of slide 37. This is achieved by use of the lost motion device coupling piston rod 63 to slide 37. Such a lost motion device is deemed advantageous since the inclined abutting surface angle on slide 37 is a self-locking taper that needs a relatively large force for unlocking crank 41 from slide 37 and overcoming the static friction therebetween. The free travel or lost linear motion between piston rod 63 and slide 37 during the return piston stroke provides a force multiplying snap or jerk action when pin 83 or headed rod (see Figure 14) engages the trailing end of transverse slot 77 thereby unlocking the self-locking mechanism.
A comparison of Figures 14 and 15 illustrate the coincidental return stroke movement of slide 37 and piston rod 63. This linearly sliding movement of slide 37 causes a toggling action (for clamping functions) or pivoting of link 39 which, in turn, pivots crank 41, hub 43 and arm 45 about a pivot axis 261 through center hole 151 (see Figure 3). Vertically slotted openings 91 allow link 39 to vertically move while encouraging a crank contact point 263 to pivotally track and clear around a radius 265 on slide 37.
Figure 16 illustrates piston rod 63 and slide 37 in their fully rearward stroke positions. Consequently, arm 45 is fully rotated away from its locked position. When pivoted back toward the position of Figure 13B, link 39 rotates crank 41 close to its final position. Slotted openings 91 in slide 37 allow contacting surfaces 123 and 125 of crank 41 to contact and abut against abutting surface 73 of slide 37. This forces crank 41 into the self-locking position wherein torquing forces are equally balanced between contacting surfaces 123 and 125 in relation to abutting surface 73 as vectored away from arm pivot axis 261. Thus, the lost motion device and slots allow for considerably wider part manufacturing tolerances as compared to conventional powered clamp components while the present invention powered apparatus still produces a precision and highly repeatable lock up gauging mechanism and powerfully toggled clamp.
The apparatus of the present invention is preferably assembled as follows: First, the components are formed then machined. Second, the hub is inserted through the cross bores of the unitary body side walls. Third, the piston rod, slide, link and a link pin are preassembled outside of the body as a subassembly. Next, the subassembly is inserted through the front opening of the body. Fifth, the crank is placed into the hub lateral channel by way of the body front opening whereafter, the crank is pinned to the hub. Sixth, the piston is inserted into the piston bore and then joined to the piston rod. Seventh, the end cap is screwed onto the body. Subsequently, after insertion of grease into the body cavity, the front cover is screwed onto the body. Finally, the arm is positioned in relation to the body wherein the dowels are inserted and nut is torqued upon the screw.
Referring now to Figure 18, a second alternate embodiment of the present invention powered clamp 31 can be fastened to a moving table, such as a rotary or horizontally sliding table, for retaining a workpiece such as a pipe 281. Accordingly, a moving arm 283, coupled to a hub, crank, link, slide and actuator 285, holds pipe 281 against a stationary arm 287. Distal ends of arms 283 and 287 are provided with semi-cylindrical recesses 289 for engagably receiving and holding pipe 281.
A third alternate embodiment of the powered clamp 31 of the present invention can be observed in Figure 19. In this exemplary embodiment, an elongated moving arm 291 has a pair of opposed C-shaped gripping elements 293 and 295 which are suitably configured to retain an automotive vehicle body side panel 297 such as a door panel, quarter panel, front fender or the like. Arm 291 lifts and locks, or locates panel 297 for further gauging or machining operations, or assembly. Arms 291 and 283 (see Figure 18) are locked and moved by power transmission components as previously discussed heretofore with regard to the preferred embodiment. Furthermore, any of these disclosed present invention embodiments can be used to provide a precision pallet gage lock, a die set up position latch and safety lock, a hand or manual operated clamp part locator with a manually actuable pull handle, a taper lock mechanism for operation of a gear and rack to position and lock a slide, a folding furniture lock, window locks, precision valve opening for flow measurement, and precise opening and closing a pair of opposing mechanisms.
The powered clamp of the present invention has further advantageous features. The powered clamp of the present invention has a single style hub for left, right or dual arm clamps. This hub allows arm position changing without disassembly of the internal mechanism. Any arm can be mounted in any of the standard eight positions at 45° increments or, alternately, other specially machined locations and arm angles can be provided. Additionally, the present invention encourages simplified arm mounting or changeover using the single socket head cap screw, thereby eliminating pressed-on arms and jack screws,h or set screw retention. The traditional necessity for a precision octagon broached hole in the arm is also eliminated. Thus, the present invention apparatus exhibits increased load bearing capability at a lower manufacturing cost compared to the octagon hub and arm patterns. The dowel pins may also be made as shear pins for protection of equipment.
While various embodiments of this powered clamp and gauging apparatus have been disclosed, it will be appreciated that various modifications may be made without departing from the present invention. For example, the slide, link, crank, hub and arm may be partially or totally disposed external from a body. Although not achieving many of the performance, cost and weight benefits of the present invention, various other actuating mechanisms may be employed to move the slide such as electric motors, internal combustion motors or manual actuation in combination with a rack and pinion mechanism, gears, pulleys, screw drives or the like. Moreover, the moving arm may have many differing shapes for engaging or holding a variety of work pieces or instruments. The specific shapes and moving motions of the slide, link and crank can be modified or combined while maintaining various of the other novel aspects of the present invention. Various materials and manufacturing processes have been disclosed in an exemplary fashion, however, other materials and processes may of course be employed. It is intended by the following claims to cover these and any other departures from the disclosed embodiments which fall within the scope of this invention.

Claims

An apparatus (31) for positioning or clamping a workpiece, the apparatus comprising:

a body (33);

a generally linearly movable powered actuator (35) disposed in said body (33);

a movable slider block (37) coupled to said actuator (35) for movement in advancing and retracting directions,

a link (39) pivotally coupled to said slider block (37);

a crank (41) pivotally coupled to said link (39); and

a work-engaging arm (45) coupled to said crank (41) and extending exteriorly from said body (33); and

wherein said crank (41) is rotatively supported by said body (33) for rotation about a fixed axis;
characterised in that a first stop surface (73) is located on said slider block, said crank (41) having a second stop surface (123) engagable with said first stop surface (73) on said slider block (37), wherein said first stop surface (73) on said slider block (37) and said second stop surface (123) on said crank (41) are adapted to engage against each other and to cooperate with said fixed axis to at least temporarily limit rotation of said crank (41) in both the advancing and retracting directions.
An apparatus as claimed in claim 1, further comprising a guiding surface on said body (33) for guiding the movement of said slider block (37), said guiding surface being arranged to oppose the forces exerted on said slider block by said second stop surface (123) when said slider block (37) is fully advanced.
An apparatus as claimed in claim 2, wherein said guiding surface is disposed on the opposite side of said slider block (37) from said first stop surface (73).
An apparatus as claimed in any one of the preceding claims, wherein said first stop surface (73) is slightly inclined with respect to the axis of movement of said slider block.
An apparatus as claimed in claim 4, wherein the interface between said first and second stop surfaces (73, 123) when said slider block (37) is fully advanced is a frictional self-locking taper.
An apparatus as claimed in any one of the preceding claims, further comprising a source of power and a lost motion connection between said source of power and said actuator.
An apparatus as claimed in any one of the preceding claims, wherein said slider block (37) and crank (41) are bifurcated to pivotally receive said link (39).
An apparatus as claimed in any one of the preceding claims, further comprising a third stop surface (125) on said crank (41) spaced from said second stop surface (123) which is also engageable with said slider block (37) when it is fully advanced.
An apparatus as claimed in claim 8, wherein said third stop surface (125) is arranged to engage said first stop surface (73).
An apparatus as claimed in any one of the preceding claims, wherein said crank (41) includes a hub (43) rotatively supported by said body (33).
An apparatus as claimed in claim 10, wherein said crank (41) is fixedly connected to said hub (43) by a plurality of pins (171, 172) disposed generally parallel to the rotational axis of said hub.
An apparatus as claimed in claim 10, wherein said arm (45) is fixedly located with regard to said hub (43) by at least one pin (171, 172) disposed in a pin-retaining hole (175) in said arm, said arm having a plurality of said pin-receiving holes therein so that orientation of said arm with regard to said hub can be relatively varied by the choice of holes used.
An apparatus as claimed in claim 12, wherein said arm (45) is located with regard to said hub (43) by a plurality of said pins (171, 172).
An apparatus as claimed in claim 13, wherein said arm (45) is affixed to said hub (43) by a threaded fastener (173).
An apparatus as claimed in any one of the preceding claims, wherein said apparatus is mounted on a rotary table.
An apparatus as claimed in any one of the preceding claims, further comprising a specially contoured work engaging retainer affixed to said arm.
A method of operating a workpiece engaging device, the method comprising the steps of:

(a) moving a first member (37) in a first direction in response to an actuator (35) applying an actuating force;

(b) moving a second member (41) in a second and rotational direction about a fixed axis in direct response to movement of said first member (37);

characterised in that the method includes the following step:

(c) stopping the rotation of said second member by rotating the second member until said second member (41) abuts against said first member (37) to at least temporarily lock said second member against rotation in both the advancing and retracting directions regardless of the presence of an actuation force.
The method of claim 17, wherein said first member (37) slides in a linear direction when pneumatic pressure is applied to a piston (61) coupled to said first member (37).
The method of claim 17 further comprising rotating an arm (45) with said second member (41), said arm being removably attached to said second member with said axis extending through both of said second member and said arm.
The method of claim 17, wherein a frictional self-locking relationship is created between said first and second members (37,41).
The method of claim 20, further comprising the step of causing said actuator (35) to apply a retracting force on said first member (37) utilizing a lost motion connection to facilitate unlocking of said second member (41).
The method of claim 17 further comprising the steps of:

(a) forming a hollow, unitary body (33);

(b) inserting a hub (43) into a cross bore in said body (33);

(c) preassembling a piston rod (63) and link (39) to a slider block (37) as a subassembly;

(d) inserting said subassembly (37,39,63) through a front opening of said body;

(e) inserting said second member (41) into said front opening of said body (33);

(f) attaching said second member (41) to said hub (43); and

(g) attaching said second member (41) to said link (39).
The method of claim 22 further comprising the steps of:

(a) pinning said second member to said hub;

(b) inserting grease through said front opening of said body; and

(c) attaching a front cover to said body to seal said front opening.